US3306302A - Threshing assembly - Google Patents

Threshing assembly Download PDF

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Publication number
US3306302A
US3306302A US365062A US36506264A US3306302A US 3306302 A US3306302 A US 3306302A US 365062 A US365062 A US 365062A US 36506264 A US36506264 A US 36506264A US 3306302 A US3306302 A US 3306302A
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United States
Prior art keywords
cylinder
shaft
threshing
force
assembly
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US365062A
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English (en)
Inventor
Mark Alexander Hing
Necas Joseph
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
AGCO Ltd
Original Assignee
Massey Ferguson Ltd
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Filing date
Publication date
Application filed by Massey Ferguson Ltd filed Critical Massey Ferguson Ltd
Priority to US365062A priority Critical patent/US3306302A/en
Priority to GB18218/65A priority patent/GB1102570A/en
Priority to SE5759/65A priority patent/SE305563B/xx
Priority to ES0312556A priority patent/ES312556A1/es
Application granted granted Critical
Publication of US3306302A publication Critical patent/US3306302A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • A—HUMAN NECESSITIES
    • A01—AGRICULTURE; FORESTRY; ANIMAL HUSBANDRY; HUNTING; TRAPPING; FISHING
    • A01F—PROCESSING OF HARVESTED PRODUCE; HAY OR STRAW PRESSES; DEVICES FOR STORING AGRICULTURAL OR HORTICULTURAL PRODUCE
    • A01F12/00—Parts or details of threshing apparatus
    • A01F12/18—Threshing devices

Definitions

  • This invention relates to agricultural threshing machines and more particularly concerns a cylinder-concave assembly for such machines.
  • Another object is to provide an assembly of the above kind which allows accurate, easily made adjustment of the spacing or clearance between the cylinder and the concave of the assembly so that the proper setting for the nature, condition and density of the crop can be readily attained.
  • a further object is to provide an assembly as characterized above with a compact control mechanism which is sturdy and smoothly operable so as to be well suited for commercial manufacture and practical use.
  • FIGURE 1 is a fragmentary perspective of a combine embodying the invention and having portions broken away for clarity;
  • FIG. 2 is an enlarged longitudinal section through the concave and grate assembly of the combine shown in FIG. 1;
  • FIG. 3 is an enlarged section taken approximately along the line 33 in FIG. 2;
  • FIG. 4 is a section taken approximately along the line 4-4 in FIG. 3;
  • FIG. 5 is an enlarged fragmentary section of portions of the cooperating concave and cylinder otherwise shown in FIG. 2;
  • FIG. 6 is a fragmentary elevation of the portion of the cylinder shown in FIG. 5.
  • FIG. 1 there is shown a portion of a combine 10 embodying the invention and including a frame 11, diagrammatically illustrated, which supports a header assembly 12, a threshing and separating assembly 13 and a cleaning assembly 14.
  • the header assembly 12 includes a reel 15 which revolves above a cutter bar 16 so that the crop is gathered, harvested and fed rearwardly to a table auger 17 that feeds the harvested mass to a floating elevator 18.
  • the threshing and separating assembly 13 includes a generally conical grate concave 20 and a generally conical cylinder 21 journalled coaxially within the concave.
  • the harvested mass is fed to the assembly 13 through an opening 22 in the lower front portion of the-concave 20.
  • the cylinder 21 is driven in a counterclockwise direction as seen in FIG. 1 with power being supplied from a transmission 23 connected by a belt 24 to a transverse shaft 25 which is coupled to a cylinder pulley 26 by a belt 27.
  • the harvested mass is driven around and axially between the concave 20 and the cylinder 21 so that the mass ice moves in -a generally helical path counterclockwise and to the left as viewed in FIG. 1.
  • the straw is discharged rearwardly and downwardly through a chute 30 and the separated grain passes through the concave 20 and is directed to the cleaning assembly 14.
  • the cleaning assembly 14 includes shaker shoe sieves or screens 31 and 32 which cooperate with a fanning mill, not shown, to clean the grain by blowing chaff and foreign material out with the straw through the chute 30.
  • the grain passes downwardly and is transferred by an auger 33 to an elevator and cross auger assembly 35 that is effective to deliver the grain to the desired storage point.
  • the threshing cylinder 21 is formed of a plurality of peripheral, axially extending rasp bars 40 mounted on support disks 41 (see FIG. 2). Stifiener plates 42 are provided to strengthen the cage-like structure of the threshing cylinder 21.
  • the rasp bars are formed with grooves 43 on their outer surfaces which are angled so as to impart a helical path producing driving force on the harvested mass. That is, particles P of the harvested mass (see FIG. 6) are struck by the edge of the grooves 43 as the rasp bar rotates in the direction of the arrow 44 so as to exert a glancing blow in the approximate direction of the arrow 45. This tends to impel the particle P in the desired generally helical path.
  • the cylinder 21 is formed with a slightly greater conical angle than the concave 20 so that the space between these elements, within which the threshing takes place, converges, as best seen in FIG. 2.
  • the convergence of the conical threshing region tends to maintain a more uniform cross sectional area through which the crop material flows since the increasing diameter of the crop flow path is offset by the convergence or narrowing down of the threshing region.
  • a decreasing cross sectional area is desirable since the velocity of the crop material increases as the diameter of its flow path increases, and the reduced cross sectional area in the threshing region tends to maintain a more uniform density of crop material throughout the length of the cylinder Also, there is a slight reduction in the mass of the crop material as grain is separated out, and the decreasing cross section-a1 area compensates for this and maintains a more uniform density of the crop material being treated. The uniform density insures more uniform threshing and separating.
  • the cylinder 21. is mounted for axial shifting movement and provision is made for'yieldably counter-balancing the axially directed forces acting on the cylinder when it is in normal operation so as to hold the cylinder in a neutral axial position.
  • the yieldable force can be overcome and, hence, the cylinder is able to shift axially toward the right in FIG. 2 to increase the clearance between the cylinder and the surrounding concave 20 when there is an increase in axial force on the cylinder exerted in that direction.
  • 3 stub shaft 56 carries the pulley 26 and hence the stub shaft is rotatably driven.
  • a cylinder shaft 58 is mounted coaxially with the stub shaft 56 for both rotation and axial movement.
  • the shaft 58 is tubular and rigidly carries an end cap 59.
  • a sleeve 60 is piloted over the end of the stub shaft 56 and formed with a flange 61 that is securely bolted to the end cap 59.
  • the cylinder 21 is mounted for axial movement on the shaft 58 through collars 63 and 64 which mount two of the support disks 41 that carry the rasp bars 40 of the cylinder.
  • the collar 63 is slidably fitted on the sleeve 60 and the collar 64 is slidably splined on a spline portion 65 of the cylinder shaft 58.
  • the opposite sides of the cylindrical portion of the sleeve 60 are formed with axially extending splines 66 and 67, and there are opposed axially extending splines on both the collar 63 and the stub shaft 56.
  • balls 67 Keyed in the opposed splines are sets of balls 67 so that the balls transmit torque between the stub shaft 56 and the surrounding sleeve 60, and between the sleeve 60 and the surrounding collar 63. Also, the balls permit free relative axial movement between the parts.
  • the balls 67 are loosely retained in spaced position by rod-like spacers 68, and snap rings 69 hold the parts in assembled relation.
  • a plurality of helical springs 70 are compressed between the collar 63 and adjustable seats 71 threadably secured on rods 72 which are fixed with respect to the cylinder shaft 58.
  • the springs 70 fit over the rods 72 and the rods pass freely through the collar 63 loosely carrying seats 73 which anchor the ends of the springs 70 that act on the collar.
  • the threaded seats 71 are held in adjusted position by jam nuts 74 and the rods 72 are anchored by being passed through the sleeve flange 61 and the end cap 59, with these latter parts being tightly sandwiched between the threaded portion of the rod and securing nuts 75.
  • the cylinder 21 is free to move axially to the right as seen in FIGS. 2 and 3 against the force exerted by the springs 70 with the collar 63 rolling easily over the sleeve 60.
  • the neutral operating position toward which the springs 70 urge the cylinder 21 is established by a stop ring 77 fixed in a peripheral groove formed in the sleeve 60 and against which the collar 63 abuts.
  • a threaded rod 78 is threadably fitted in the end cap 59 of the cylinder shaft 58 and is rotatably anchored in the stub shaft 56.
  • An end of the rod 78 extends from the end of the stub shaft 56 and is formed with a wrench receiving head 79 so that the rod may be easily turned from outside of the frame 11 so as to threadably shift the cylinder shaft 58, and thus the sleeve 60, axially with respect to the stub shaft 56.
  • This varies the axial position of the stop ring 77 and, hence, changes the neutral position of the cylinder 21 without, of course, varying the force exerted by the springs 70. Because of the balls 67, the sleeve 60 rolls freely in an axial direction on the stub shaft 56.
  • a second axial force acting on the cylinder 21 is the acceleration force. This is the reaction by the harvested mass to the accelerating force exerted on the particles of the mass in the direction of the arrow 45.
  • the reaction of each harvested mass particle P on the edge of the grooves 43 has a circumferential component 80 and an acceleration force component 81 which tends to shift the cylinder 21 to the left as seen in FIG. 2.
  • the magnitude of the acceleration force varies directly with cylinder r.p.m., varies directly with the angle at which the grooves 43 are formed, varies directly with an increasing load of harvested mass acted on by the cylinder, and has a slight inverse relationship to the conical angle of the cylinder.
  • the third force to consider is the squeeze force caused by pressing material between the converging conical cylinder 21 and the surrounding conical concave 20. Squeezing a mass M between the concave and the cylinder (see FIG. 5) develops a reaction force 82 against the cylinder that has a radially extending component 83 and a squeeze force producing component 84. The squeeze force thus tends to shift the cylinder 21 toward the right as seen in the drawings and it will be evident that the magnitude of the squeeze force varies directly with the amount of harvested mass being pressed between the cylinder and concave, varies directly with the conical angle of the cylinder, and varies directly with the amount of convergence or narrowing down of the threshing region between the cylinder and the surrounding concave.
  • the force of the springs 70 is exerted on the cylinder so as to shift it toward the left in opposition to the no load force and the squeeze force, and in the same direction of the acceleration force. This, however, is simply because in a particular workable embodiment the summation of the no load force and the squeeze forces were greater, under normal operating conditions, than the acceleration forces. If different parameters are chosen in the design of the threshing assembly, it is possible that the acceleration force would exceed the no load and squeeze forces so that the springs would have to act in the opposite direction to yieldably hold the cylinder in a neutral position.
  • a working embodiment of the invention was constructed in which the cylinder was seventy-nine inches long with a small end diameter of fifteen inches and a large end diameter of twenty-six inches.
  • the conical angle was eleven degrees, sixteen minutes.
  • the cylinder of this dimension was mounted in a conical concave having a small end diameter of seventeen and one half inches and a large end diameter of twenty-six and a quarter inches, the conical tangle of the concave being ten degrees.
  • the rasp bar grooves 43 were disposed at an angle of thirty degrees from a radial plane.
  • the total force exerted by the springs 70 can be set at approximately 200 pounds in the example given so as to hold the cylinder :in a normal neutral position and permit normal efficient threshing under full load conditions. If slugging occurs, the squeeze force rises so that the spring 70 yield to permit the cylinder to clear itself.
  • the multiple function control mechanism 55 is a particularly compact and sturdy unit capable of smooth reliable operation and hence well adapted for commercial manufacture and use.
  • the axial adjustment permitted by the rod 78 sets the neutral position of the cylinder and the initial clearance between the cylinder and the concave so as to give the operator of the combine control of threshing effectiveness for crops of varying nature, condition and density.
  • a threshing cylinder assembly comprising, in combination, a frame, a rotatably driven stub shaft journalled in said frame, a cylinder shaft mounted in said frame coaxially with said stub shaft for bot-h rotation and axial movement, a threshing cylinder mounted on said cylinder shaft, means interconnecting said stub shaft and said mounting shaft for selectively varying the axial position of said mounting shaft, and means interconnecting said stub shaft and said cylinder for simultaneous rotation.
  • a threshing cylinder assembly comprising, in combination, a frame, a rotatably driven stub shaft journalled in said frame, a cylinder shaft mounted in said frame coaxi-ally with said stub shaft for both rotation and axial movement, a threshing cylinder mounted for axial movement on said cylinder shaft, means for yieldably holding said cylinder in a neutral axial position on said shaft,
  • a threshing cylinder assembly comprising in combination, a frame, a rotatably driven stub shaft journalled in said frame, a cylinder shaft mounted in said frame coaxially with said stub shaft for both rotation and axial movement, a threshing cylinder mounted for axial movement on said cylinder shaft, means including adjustably prestressed springs for yieldably holding said cylinder in a neutral axial position on said cylinder shaft, a threaded rod interconnecting said stub shaft and said cylinder shaft for selectively varying the axial position of said cylinder shaft, and means including opposed axially extending splines with interfitting balls for keying said stub shaft and said cylinder together for simultaneous rotation while permitting free relative axial movement.
  • a threshing assembly comprising, in combination, a conical concave, a conical cylinder journalled coaxially within said concave, means for rotatably driving said cylinder, said cylinder being mounted for axial shifting movement to a selected neutral position, and means for yieldably counterbalancing the axially directed forces acting on said cylinder when in normal operation so as to hold the cylinder in said neutral position, said counterbalancing means yielding so that said cylinder can move axially to increase the clearance between the cylinder and said concave upon increases in axial force in that direction.

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  • Life Sciences & Earth Sciences (AREA)
  • Environmental Sciences (AREA)
  • Threshing Machine Elements (AREA)
  • Harvester Elements (AREA)
  • Outside Dividers And Delivering Mechanisms For Harvesters (AREA)
US365062A 1964-05-05 1964-05-05 Threshing assembly Expired - Lifetime US3306302A (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
US365062A US3306302A (en) 1964-05-05 1964-05-05 Threshing assembly
GB18218/65A GB1102570A (en) 1964-05-05 1965-04-30 Threshing mechanism
SE5759/65A SE305563B (es) 1964-05-05 1965-05-03
ES0312556A ES312556A1 (es) 1964-05-05 1965-05-04 Una maquina agricola trilladora y separadora.

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US365062A US3306302A (en) 1964-05-05 1964-05-05 Threshing assembly

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US3306302A true US3306302A (en) 1967-02-28

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US365062A Expired - Lifetime US3306302A (en) 1964-05-05 1964-05-05 Threshing assembly

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US (1) US3306302A (es)
ES (1) ES312556A1 (es)
GB (1) GB1102570A (es)
SE (1) SE305563B (es)

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3410270A (en) * 1965-02-06 1968-11-12 Massey Ferguson Gmbh Adjustable threshing assembly
US3426760A (en) * 1965-11-23 1969-02-11 Massey Ferguson Inc Toothed conical threshing assembly
US4087953A (en) * 1976-10-28 1978-05-09 Deere & Company Combine crop feeding system
US4108150A (en) * 1977-03-23 1978-08-22 Allis-Chalmers Corporation Agitator for an axial flow cylinder
DE2807945A1 (de) * 1977-03-01 1978-09-07 Univ Adelaide Dreschmaschine
US4139013A (en) * 1977-10-20 1979-02-13 Deere & Company Threshing rotor for a combine
US4154250A (en) * 1978-03-03 1979-05-15 Allis-Chalmers Corporation Drive mechanism and support arrangement for agitator of axial flow threshing cylinder
US4222395A (en) * 1979-04-30 1980-09-16 Allis-Chalmers Corporation Threshing cage fingers for retarding the flow of material through an axial flow harvester
US4249542A (en) * 1979-12-20 1981-02-10 Schuler Murry W Combine
US6468152B2 (en) 2001-03-02 2002-10-22 Deere & Company Rotary combine having a frusto-conical rotor housing
US20110070933A1 (en) * 2009-09-18 2011-03-24 Jean Imbert Threshing system including threshing elements having openings for grain passage
US20190069490A1 (en) * 2017-09-07 2019-03-07 Claas Selbstfahrende Erntemaschinen Gmbh Combine harvester
US20190069487A1 (en) * 2017-09-07 2019-03-07 Claas Selbstfahrende Erntemaschinen Gmbh Combine harvester
US20190223383A1 (en) * 2018-01-22 2019-07-25 Cnh Industrial America Llc Free-rolling rotor cage

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108012672B (zh) * 2018-01-03 2023-10-03 苏州萨伯工业设计有限公司 带有伺服反馈控制功能的动态平衡脱粒装置

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1029451A (en) * 1910-05-13 1912-06-11 Charles Mckee Corn-sheller.
US1096554A (en) * 1913-03-19 1914-05-12 James W Morrison Corn-sheller.
US2325654A (en) * 1939-12-23 1943-08-03 Kalb Agricutural Ass Inc De Corn sheller
US2484228A (en) * 1943-12-13 1949-10-11 Isay Rudolf Corn shelling machine with adjustable concave

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1029451A (en) * 1910-05-13 1912-06-11 Charles Mckee Corn-sheller.
US1096554A (en) * 1913-03-19 1914-05-12 James W Morrison Corn-sheller.
US2325654A (en) * 1939-12-23 1943-08-03 Kalb Agricutural Ass Inc De Corn sheller
US2484228A (en) * 1943-12-13 1949-10-11 Isay Rudolf Corn shelling machine with adjustable concave

Cited By (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3410270A (en) * 1965-02-06 1968-11-12 Massey Ferguson Gmbh Adjustable threshing assembly
US3426760A (en) * 1965-11-23 1969-02-11 Massey Ferguson Inc Toothed conical threshing assembly
US4087953A (en) * 1976-10-28 1978-05-09 Deere & Company Combine crop feeding system
DE2807945A1 (de) * 1977-03-01 1978-09-07 Univ Adelaide Dreschmaschine
US4108150A (en) * 1977-03-23 1978-08-22 Allis-Chalmers Corporation Agitator for an axial flow cylinder
US4139013A (en) * 1977-10-20 1979-02-13 Deere & Company Threshing rotor for a combine
FR2406383A1 (fr) * 1977-10-20 1979-05-18 Deere & Co Ensemble de traitement pour machines de battage, notamment pour moisonneuses-batteuses
US4154250A (en) * 1978-03-03 1979-05-15 Allis-Chalmers Corporation Drive mechanism and support arrangement for agitator of axial flow threshing cylinder
US4222395A (en) * 1979-04-30 1980-09-16 Allis-Chalmers Corporation Threshing cage fingers for retarding the flow of material through an axial flow harvester
FR2472910A1 (fr) * 1979-12-20 1981-07-10 Schuler Murry Dispositif de battage d'une moissonneuse-batteuse a ecoulement axial
US4249542A (en) * 1979-12-20 1981-02-10 Schuler Murry W Combine
US6468152B2 (en) 2001-03-02 2002-10-22 Deere & Company Rotary combine having a frusto-conical rotor housing
US6884161B2 (en) 2001-03-02 2005-04-26 Deere & Company Rotary combine having a frusto-conical rotor housing
US20110070933A1 (en) * 2009-09-18 2011-03-24 Jean Imbert Threshing system including threshing elements having openings for grain passage
US8142266B2 (en) 2009-09-18 2012-03-27 Cnh America Llc Threshing system including threshing elements having openings for grain passage
US20190069490A1 (en) * 2017-09-07 2019-03-07 Claas Selbstfahrende Erntemaschinen Gmbh Combine harvester
US20190069487A1 (en) * 2017-09-07 2019-03-07 Claas Selbstfahrende Erntemaschinen Gmbh Combine harvester
US10820517B2 (en) * 2017-09-07 2020-11-03 Claas Selbstfahrende Erntemaschinen Gmbh Combine harvester cleaning device
US10827681B2 (en) * 2017-09-07 2020-11-10 Claas Selbstfahrende Erntemaschinen Gmbh Combine harvester including a cleaning device to segregate harvested material
US20190223383A1 (en) * 2018-01-22 2019-07-25 Cnh Industrial America Llc Free-rolling rotor cage
US10674672B2 (en) * 2018-01-22 2020-06-09 Cnh Industrial America Llc Free-rolling rotor cage

Also Published As

Publication number Publication date
GB1102570A (en) 1968-02-07
ES312556A1 (es) 1966-02-01
SE305563B (es) 1968-10-28

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